Automatic ironing machine



A. H. GERHARDT ETAL AUTOIATIC IKONING MACHINE Original Filed April 23, 1943 12 Sheets-Sheet 1 8 H. Y 8 u! In B 1 I, v. E I .M W n 1 I I Q 3 n3 .nlll Q 1! Q 7 0\ A: 3 3 t2 i Q, 3 fi "U, MN. H H H HmwHH HWHHWWH li r i l IQ} {mm l ml Pl l E a t 5 an M Feb. 12,1946

Feb. 12, 1946. A. H. GERHARDT ETAL AU'IOIATIQ IROHIHG IAQHINE Original Filed April 2:5, 194:; 1'2 Sheets-Sheet s i. I x W Feb. 12,1946- A. H. GERHARDT ET AL 22,720

AUTOMATIC IRQNING MAHINE v Original Filed April 23, 1945 12 Sheets-Sheet 4 ,Feb. 12, 1946. A. a GERHARDT Emu; 22,720 I AUTOIATIG IRONIHG CHINE Original Filgd Api'il 23, 1943 12 Sheets-Sheet 5 Feb. 12, 1946. A. H. GERHARDT ET AL Re. 22,7

AUTOMATIC IRQNING MACHINE Original Filed April 23, 1943 12 Sheets-Shet 6 A. H. GERHAFDT ETAL Feb. 12, 1946.

AUTOMA'IQI'C IRONIFNG MACHINE Original Filed April 23 1943 12 SheetsSheet Feb. 12,19 6. I A. H. GERHARDT ET AL 22,720

AUTOMATIC IRONING MACHINE Original Filed April 23, 1947 12 Sheets-Sheet 9 A. H.IGERHA'RDT ET AL Re. 22,720

AUTOMATIC IRONING MACHINE Original Filed April 23, 1943 12 Sheets-Sheet 11' we a.

Feb.- 12, 1946.

1946- i H; GERHA D T AL R. 22,720

' AUTOMATIC IRQNING MACHINE Original Fi ed April 23, 1943 12 she ts-s eet 12 f Reissued set. 12, 1946 v Re. 22,120

Maher, Chicago,

corporation of Illinois Original No. 2,372,775, dated April 3, 1945, Serial No. 484,182, April 23, 1943.

I, 11]., assignors to Electric Household Utilities Corporation,

Chicago, 11]., a

Application for 11':-

issue November 23, 1945, Serial N0. 630,304

20 Claims.

This invention relates to power operated ironingmachines of the domestic type. including a rotatable roll element totally supported at one end, and a cooperating electrically heated shoe element. More particularly, the present invention is directed to ironing machines of the automatic type, wherein the roll element is motor power driven, and wherein one of the elements is moved by motor power into and out of cooperating engagement with the other element. In the machine herein disclosed, the shoe element is power moved into and out of cooperative engagement with the roll.

Machines of this general class have heretofore been made in two main types, one being a portable machine oi a size and weight for convenient handling and renioval from place to place. or for One of the objects of this invention is provide in an ironing machine of the character indicated. a novel drive arrangement for operating the roll and shoe independently of each other, so that at no time is the power of the motor utilized for simultaneously operating both the roll '35 and the shoe, thus permitting the use of a relatively small and light weight motor.

Another object is to provide an improved drive mechanism for an automatic ironing machine,

including separate drive connections for operating 40 the roll and the shoe, and wherein said separate drive connections are operably connected respectively to the oppos te ends of the motor shaft and are interconnected in a manner to preclude simultaneous operation 01 the'roll and shoe.

A further object is to provide a simplified conconnections for selectively operating separate drive connections from the motor for actuating the roll and the shoe, and wherein the control member is adapted to be moved in a cyclic manner to cause sequential operation of the shca and the roll, and by virtue of which operation of the single control member can selectively cause any ofthe following effects: first, roll rotating with shoe engaged therewith; second, roll stopped with shoe engaged therewith; and third, roll stopped and shoe disengaged therefrom.

And still another object is to provide an improved drive mechanism for an automatic ironer, which permits utilizing a motor of relatively small power and relatively light weight.

A still further object is to provide in an ironing machine oi. the type having driving connections from one end of a motor for rotating the roll, together with connections by virtue of which the shoe may be moved toward or away from the roll, together with a novel, unitary drive mechanism adamed to be manufactured as a separate unit, and which may be quickly and easily interconnected with the roll driving connections for converting a machine of the type having a handoperated shoe into an automatic ironer, wherein p the shoe is moved by motor pcwer.

Other objects and advantages of this invention will be apparent from the following description, taken in connection with the accompanying drawings, in which:

Fig. 1 is a front elevational view of the ironing machine embodying the present invention, with *5 condition of the machine, wherein .the shoe is in trol mechanism for an automatic ironing ma- 7 chine, including a single control member adapted to be, manipulated by the operator for selectively controlling the application of the power of the driving motor for actuatingi the roll and the shoe.

Still another object is to provide a novel and simplified operator actuated control mechanism,

engagement with the roll, and wherein theroll is stopped.

Fig. 4 is a fragmentary sectional view, of the clutch mechanism seen in Fig. 3, showing a condition of the mechanism when the shoe is rotating and the shoe is in pressure engagement with the roll. a

Fig. 5 is a transverse sectional view through the roll drive clutch, taken substantially as indiincluding a single control member, together with cated at line 5-5 on Fig. 4.

aavao the outer end ofthe shoe driving mechanism, taken as indicated at line 22-22 on Fig. 18.

Fig. 23 is a detail view, part in section and 1 part in elevation, taken substantially as indicated at line 28-28 on Fig. 21.. V

Fig. 24 is a sectional view similar to Fig. 19,

- showing the clutch in engaged poMtion.

Fig. 10 is a bottom elevational view of the linkage and part of the control mechanism for controlling the movement or the shoe toward and away from the roll, with the parts shown in a condition of adjustment corresponding to pressure engagement of the shoe against the roll, and with the roll rotating.

Fig. 11 is a view similar to Fig. 10 showing the position or the parts corresponding to the shoe engaging the roll, and the roll stopped.

Fig. 12 is a view similar to Fig. 10 and represents an intermediate position of the parts as occurs between the position of adjustment of the parts represented in Figs. 11 and 13.

Fig. 13 is a view similar to Fig. 10 showing the parts in a position of adjustment corresponding to the shoe out of engagement with the roll, and the roll stopped. a

Fig. 14 is an end elevational view of-the control linkage and shoe operating mechanism, taken substantially as indicated at line ll-ll on Fig. 13, and corresponding to a position at which the shoe is away from the roll, and the roll stopped. Y

Fig. 15 is a detail view of the shoe operating cam and associated parts, shown in another position 01' adjustment from that illustrated in Fig. 14, and corresponding to a position at which the shoe is .against the roll, and the roll is rotating.

Fig. 16 'is an enlarged, detail view of the knee control member, shown operably connected to the linkage and driving mechanism for actuating the shoe under motor power, into and out of pressure engagement with the roll, and for driving the roll.

Fig. 17 is a detail sectional view through '9. portion of the control linkage, taken as indicated at line l|l| on Fig. 10.

Fig. 18 is a transverse, staggered, sectional view, with certain parts shown in elevation,

through the power drive mechanism for actuating the shoe, taken substantially as indicated at,lines l8l8 on. Fig. 1, and lines l8-l8 on Fig. 19. I

Fig. 19 is a sectional view' through the shoe driving mechanism, taken substantially as indicated at line. l8l8 on Fig. 18, and showing the driving clutch disengaged.

Fig. 20 is a transverse, staggered, sectional view throtlgh the shoe operating mechanism, 1taker;substantially as indicated at line 20-40 on I Fig. 21 is a fragmentary sectional view through a portion of the shoe driving mechanism, taken substagtiaily as indicated at line 2l-2l on Fig.

Fig. 22 is a transverse, axial section th gh Fig. 25 is a transverse, staggered, fragmentary, sectional view through parts of-the shoe driving mechanism, taken substantially as indicated at line 25-28 onFig. 24, and showing the tripping disc and finger.

Fig. 26 is a side elevational view of the tripping disc or the shoe operating mechanism.

2'7 is a face view of the tripping disc, taken as indicated at line 21-41 on Fig. 26.

Fig. 28 is a staggered, sectional view, part in section and part in elevation, through the shoe supporting arm, and associated parts, with the shoe shown in pressure engagement with the roll, and the dot line position indicating the shoe away from the roll.

Fig. 29 is a vertical, sectional view through the shoe arm support, taken as indicated at line 29-48 on Fig. 28.

Fig. 30 is a transverse, sectional view, part in section and part in elevation, through a portion of the emergency release mechanism, taken as indicated at line -40 on Fig. 28.

Fig. 31 is a view similar to Fig. 28 with the shoe supporting arm shown in section, and the emergency release in operated condition, disposing the shoe out of operative pressure engagement with the roll.

Fig. 32 is a sectional view through the shoe arm support in emergency released condition, taken substantially as indicated at line 32-32 on Fig. 31. i

Fig. 33 is a sectional view similar to Fig. 30,

but showing a portion of the emergency release in a released condition.

Referring now in detail to the drawings, the machine proper includes a supporting frame in the form of a hollow housing or base ID, of generally rectangular form, at the right hand end of which is mounted an upstanding gooseneck type housing or standard I i, which serves to enclose power drive connections to and provides support for a rotary roll II. The housing In, is formed, mainly of sheet metal, and is of a generally inverted U-shaped cross-section, connected at opposite ends to cast members Ill. The standard II, as shown, is in the form of a casting, and includes an upstanding, tubular portion terminating at its upper end in a horizontal extending tubular portion, and the said upstanding and horizontal portions being joined together by suitably curved surfaces. relatively small cross-sectional dimension, and preferably, is approximately equal to, or less than, the external diameter of the roll l2, taken at any transverse plane throughout the entire length of the standard.

The roll i2 includes a tubular metal body It, around which is wrapped suitable padding material as indicated at l5, and the latter in turn is surrounded bya fabric wrapper or cover IS". The roll extends horizontally and in parallel spacedapart relation to the top of the base l0, and is totally supported at one end by the horizontal por tion of the gooseneck standard II, in a conventional manner. Cooperating with the roll I2, is a shoe I6, which is preferably electrically heated in a manner well understood in the art. The

The standard, H, is of,

operating face of the shoe is shaped to the contour of the padded roll l2, and is mounted for movement into and out of pressure engagement with the roll, as will hereinafter be described.

The metal tubular body l4, of the roll is provided at opposite ends, and at substantially centrally of its length, with dish-shaped stampings "and I8. The dish-shaped stampings H, are

provided with centrally ofl'set portions l1, formed to support bearings l9, which provide jjournal support for the roll on a metallic tube 20, which is disposed-axially within, and terminates slightly beyond the middle of the length of the roll. As may be seen at the right-hand portion of Fig. 1 of the drawings, the tube 20, extends beyond the roll into the gooseneck standard I I, and is intercentrally and longitudinally of the roll through the tube 20. and havin an end portion extending into the interior of the gooseneck standard I I, for

connection to the driving mechanism, hereinafter described, and which serves to impart driving rotary motion to the roll l2. The said end portion of the shaft within the standard II, is provided with an oil seal 24', in engagement with the inner wall of the tube 20, and said shaft is secured in proper position with respect to the roll I! and tube 20 by means of a spring collar 25, mounted on the shaft, adjacent the outer end of said tube 2!). Threaded into the outer end of the tube ill, is a nut 21, adapted to serve as an abutmentshoulder for the collar 28, to preclude outward movement of the shaft with respect to the tube 20 and the standard I I.

' an electrically driven motor 30, disposed within the sheet metal supporting base [0, adjacent the it under power into and out of cooperating engagement with the roll II. The right hand end of the motorshaft is provided with a driving pinion 40, as seen in Fig. 2 of the drawings, meshed with a gear 4|,- loosely mounted on the adjacent end of a horizontally extending shaft 43, one end of which shaft is press-fitted into a boss 44, constituting a part of the motor housing, and the other end of said shaft being slip fitted in a boss 48, formed at the outer end of the cast housin member 32, as seen in Fig. 3 of the drawings. The gear, has its hub provided with an annular groove 41, into which projects the edge of a retaining plate member 48, secured to a boss on the adjacent end of the motor housing by screws 48*. Said plate thus serves to p d a i l movement of the gear 4|, on its shaft 43. Mounted on the outer face of the gear 4|, by means of rivets 50, is a clutch plate 5|, formed with a central opening 53, the contour of which is such as to provide three circumferentially spaced-apart driving teeth 54. g

The driving mechanism for the roll is under control of a clutch mechanism which in turn is subject to interlocking control with the driving mechanism for power moving of the shoe into and out of engagement with the roll, as will hereinafter be described. The clutch mechanism is carried on the shaft 43, within a chamber 55, formed in the housing member 32, as seen in Figs. 3 and 4 of the drawings. Cooperating with the clutch plate5l, is an axially shiftable pinion 51, slidably mounted on the shaft 43. Said pinion is formed with three equidistant, circumferentially spaced teeth of greater length than the other teeth of i said pinion, as clearly seen in Fig. 4 of the drawright hand end, and having its housing securely connected to a cast housing member 32, by means or machine screws 33. The, housing 32, serves to enclose speed reducing mechanism and the lower portion of transmission mechanism, together with clutch mechanism disposed in registration with the upright leg portion of the gooseneck standard II, which mechanisms serve to supply power for operating the roll. the cast housing member 32, is formed with an pening disposed in registration with the opening formed at the lower end of the standard I l,,which in turn is in registration with a similar opening formed in the top of the sheet metal housing "I,

as seen in Figs. 1 and 2 of the drawings. The gooseneck standard is secured to the top of the support housing by means of three circumferentially spaced-apart machine screws 35, and the cast housing member 32, is rigidly connected to the lower end or the gooseneck standard II, by mean of two machine screws 31, one or which is or substantial length as seen in Fig. 2 of the draws. In the construction illustrated, power take-oil! driving connections-are provided at opposite ends of the motor shaft, and one of said connections serves to provide power for. operating the roll and the other of said connections servesto supplg power forv actuating the shoe ii, for moving The upper end of a ings, so that when said pinion is axially shifted into operative engagement with the clutch plate iii, the three long teeth are moved into cooperating relation to the driving teeth 54, of the clutch plate 5!, and by virtue of which rotary motion is thus transmitted to the pinion 51. The purpose of forming the clutch plate in the manner indicated, for cooperating with the three elongated or extended teeth on the pinion, is to avoid chattering and noise, and to, insure quick and easy entrance of the said elongated teeth into the opening in the clutch plate, intermediate it teeth 54, and thereby obtain substantially instantaneously clutching and drivin relation of the pinion and the clutch plate. Said pinion 51, at the end opposite said teeth, is formed with an elongated hub, 58, the extreme end of whichis formed with an enlarged annular flange 59, adapted to be seated into an annular socket Gil, formed in an enlarged flanged shoulder SI, of a clutch shifting collar 52, which likewise is slidiii) ably mounted on the shaft. The shoulder 6|, of said collar is provided with an opening of substantial angular extent topermit insertion of the flange 59, of the pinion 51, into the socket portion 60. The clutch pinion 51, and the shifting collar 62, together with shaft 43, are assembled together by first seating the flange 59, of pinion 51, into the socket in the shoulderlil, of the collar, and then extending the shaft 43, ,therethrough, soas to maintain the parts in coupled relation. This connection serves to reduce transmission of rotarymotion from the pinion 51, to the collar 62,

and thereby effects a reduction in strain and wear upon the element employed for shifting the collar 62.

Disposed in abutting relation to the outer endof a shoulder 65, formed at the outer end of the (511113.011 shifting collar 52, isa flanged thimble 5B,

surrounded by a coil spring 00, reacting against the flange of the thimble and against the end of the chamber 55 in the housing member 32, and thus serves to urge the clutch shifting collar 82, together with the clutch pinion 51, in an axial direction toward the motor. The extent of such inward axial movement, under influence of spring- 00, is limited by a crimped washer 10, mounted in an annular groove on the shaft 43, adjacent the outer flange 05, of the shifting collar, in a position to be engaged by the closed end of the thimble 66.

Meshing with the underside of the clutch pinion 51, is an idler gear 12, freely mounted on a stud 13, carried in a boss 14, formed as an extension of the motor housing. The lower portion- I speed reduction from the motor 30, to the driving pinion 51, when the latter is engaged with the clutch plate 5|. A further reduction in speed is obtained by mechanism which will now be described, and which also serves as the means for transmitting motion to drive the roll I2. This mechanism is in the nature of a unitary gearing assembly, and includes a vertically disposed mounting bar 16, extending upwardly intothe upright hollow leg portion of the gooseneck standard I I, with the lower portion of the bar disposed in the housing member 32, as seen in Fig. 1 of,

. the drawings. The opposite ends of the mounting bar 10, are reduced as indicated at 11, to provide trunnions, and the lower trunnion of said bar is seated in a socket 32, formed in the housing 32, while the trunnion at the upper end of said bar is seated in a socket II, formed in the interior of the upper end of the standard II, as seen in Fig. 1 of the drawings. Projecting laterally from said bar, and rigidly secured thereto, are vertically spaced-apart horizontally extending stub shafts 00, 0|, 8'2, 03, and M.

The outer end of the stub shaft 00, is fitted in a socket 32, supported in a boss on the inner wall of the housing member 32, and serves to maintain the mounting bar 16, in aligned vertical position with all of its stub shafts disposed in proper aligned relation with respect to the driving pinion 51. Loosely mounted on the stub shaft 00, is a gear 06, meshed with the clutch pinion 51, and rigidly attached to the gear 86, is a pinion 80, with which is meshed a gear 09, loosely mounted on the stub shaft 0|. mounted on the stub shaft 02, is another gear 00, which in turn is meshed with the gear 09, and rigidly attached to the gear 90, is a pinion 92, which is meshed with a gear 93, loosely mounted on stub shaft 03, and this latter gear 03,.is meshed with a gear 94, loosely mounted on the uppermost stub shaft 04. These gears are confined on their respective stub shafts in any convenient manner, and as herein shown, by means of spring U-shaped clips 16%. Rigidly connected to the uppermost gear 94, of the gear train, is a coupler member 05, of thimblelike formation, the closed end of which projects out- Loosely ward, and is formed with a socket inzthe nature of. a slot for receiving a tang-shaped terminal '22, formed on the adjacent end of the roll facturing by virtue of which the gear train may be assembled as a unit upon the mounting bar 10, prior to final assembly in the machine, and further permits utilizing a supporting standard II, of relatively small cross-sectional dimensions.

The shifting of the clutch pinion 51, by the collar 62-, for controlling the drive connections to the roll I2, is subject to the operation of control apparatus, which is in' the nature of a dual control, hereinafter described, which also serves to controlin proper sequence, the application of power for actuating the shoe into and out of cooperative engagement with the roll. For

shifting the collar 62, axially in controlling the operation ofv the clutch, there is employed a cylindrical plug or body I00, rotatably mounted in a tubular bearing provided in the housing member 32. The inner end of the plug is provided with a nubbin IOI, positioned to be moved into cooperating engagementwith the flange shoulder 65, of the clutch collar 62. The plug body I00, is retained in position in the housing 32, by a retaining plate I02, secured by screws I03, to the housing member 32, with an edge portion of the plate projecting into an annular groove I00, formed in the plug body.

Rigidly connected to they outer end of the plug body is a crank arm I05, in the form of a link, the outer end of which is pivotally connected by apivot pin I01, by a lost motion connection to one end of an operating bar I06. The operating bar I00, is rigidly connected at'its opposite end to a depending lever I00, pivotally connected at I09, to a frame member I0", of the main supporting housing I0. The lower end of the lever I08, has connected thereto, a movable control member comprising a rod 'I I I, threaded into'the lower portion of the lever I00, as seen in Fig. 16 of the drawings, and rigidly connected to the lower end of the rod III, is a depending, fiattened, knee operated member II 2. Referring now to Fig. 1 of the drawings, the knee operating member II2, normally in the starting of the machine, is in the position as indicated by dotand dash lines at A," and is adapted to be first moved to the right to the position indicated by dot and dash lines at B, and is then adapted to be returned by the action of a, coil spring III, connected to the lower end of the depending lever I08, and to the frame member I 0'', to either the position indicated by dot and dash lines at A, or to the fullline' position indicated in full lines in the drawings, which position, for convenience, is indicated at C. When the knee lever member H2, is moved from position A" to B," the operating bar I06 is moved about the pivot I09, so that the outer end of said bar moves in an upward direction, and by reason of the pivot pin I01, causes the crank arm I05, to move in clockwise direction, rotating the plug body I00, thereby causing the nubbin IN to react against the flange 65, of the collar 62, and thereby shift. the collar and the-pinion 51, outon a rock shaft I23.

wardly along the shaft 43, to disengage the pinion 51, from the clutch plate This movement takes place against the reactive force of the coil spring 63 and spring II4. In this condition of adjustment, the driving connections to the roll are broken by disengagement of the clutch, which comprises the three elongated teeth of the pinion member 51, and the clutch tions to the roll I2, still remain inoperative. I

When, however, pressure against the knee control member H2, is further relieved, said member assumes the full line position indicated at C" in Fig. 1 of the drawings, under influence of the spring H4, at which position the operating bar I06, has moved the crank arm I05, in counter-clockwise position, and the plug I00,

rotated sufllciently to move the nubbin II, to

operative relation to each other, as seen in Fig. 28

- of the drawings, includes a flanged bearing member I23, fitted into an aperture in the web portion of the arm I24, with the flange thereof, abutting against the outer surface of said arm, Slidably mounted in the bearing I26, isa stub shaft I30, one end of which projects through-an enlarged opening I20, in the web portion of the 1 arm I20, and rigidly attached to the outer end of said stub. shaft is'a handle I32.

The other endof the stub shaft I30, carries a transversely extending pin I34 on each end of which is io'urnaled a roller I35, disposed on opposite sides of the stub shaft I30. A coil spring I36, surrounds the bearing I23, and abuts at opposite ends against the adjacent surfaces of the webs of the respective arm members I20 and I24, tending to urge the arms apart. Normally, when the handle I32 is in the position seen in Fig. 2B of the drawings, the coil spring I36, is compressed, and

the rollers I35 are disposed in abutting relation to the ends of a pair of spaced apart projections relieve its pressure engagement with the shoulder 65, of the shifting collar 62, so that the spring 63, is free to move said collar 62, together with pinion 51, to dispose the elongated teeth of the pinion into meshing engagement with the clutch plate 5|, at which time the driving connections are established for imparting and transmitting rotary motion to the roll I2. The purpose of the slot I06 in .bar I06, is to provide freedom of; movement between the outer end of the operating bar I06 and the'pivot pin I01, of the crank arm i05, to accommodate the shifting relationship of the pin I01, when the crank arm I05, is moved upwardly in clockwise direction by the operating bar I06, incident to movement of the knee operating member II2, from the full line position indicated at C, to either the positions indicated at A" or B," or when the knee opcrating member is moved from the dot and dash outlined position A, to the position B.

It is to be understood that incident to such controlling movement by the knee operating member I33, extending rearwardly from the flanged portion of the bearing I28. The emergency release may be readily manipulated by turning the handle I32 through an arc of approximately 90 d grees, from the position seen in Fig. 28 to the position seen in Fig. 31, in which position the rollers I35, are disengaged from the projections I38, and disposed in a vertical plane, as seen in Figs. 31 and 32 of the drawings, in registration with the space between the projections I38. In such position of the parts, the spring I36, causes separation of the arm members I20 and I24, to the position as seen in Fig. 31 of the drawings.

- To relatch the arms in operative relation, the

H2, there is also employed other control apparatus by virtue of which the motor power, as will hereafter be described, is employed for moving the shoe I6, under power, into or out of operativ engagement with the roll I2.

Shoe supporting structure The shoe I6 is supported by a two-piece arm structure, including a main upright member I20,

of U-shaped cross section, pivotally connected at its upper end by a pivot pin I2I, to a pair of transversely, spaced-apart ears l6, on the back of the shoe I6, and the lower end of the arm I20, has its two side members I20, journal supported Fixedly mounted on the rock shaft, intermediate the side members I20, of the arm I20, is an upwardly extending, auxiliary arm I24, adapted to be normally latched to the arm I20, as seen in Fig.- 28 of the drawings, by means of an emergency release mechanism to be presently described. The lower end of the auxiliary arm I24, is provided with a splined bore for seating upon the splined outer end portion I23, of the rock shaft I23, and is fixedly secured thereon against axial movement, by means of a setscrew I26.

The emergency release mechanism, which normally latches the arm members I20 and I24 in spring I36, is compressed simultaneously with moving th arm I20, into proper relation to the arm member I24, and disposing rollers I35, beyond the ends of the projections I38, at which time the handle I32, may be rotated approximately 90 degrees, so as to dispose the rollers I35, in abutting relation to the ends of the projections I38, which serves to latch the arms in operative position. The purpose of the emergency release above described, as is well known, is to permit instantaneous disengagement of the shoe from the roll inthe event that the electrical current is suddenly cut off. Such a release is particularly important to insure against possible damage to articles in process of being ironed, in the eventv illustrated in the drawings, the shoe rock shaft proper is of relatively short length, and the shaft is desirably preloaded with spring pressure, so as to permit utilizing a motor of relatively small size and low power requirements. Referring now to Fig. 6 of the drawings, it will be seen that the end of the rock shaft, opposite the and supporting the shoe arm, is rigidly attached-such as by weldwhich in turn is journaled in the bearing MI. The outer end of the bearing plug I43, includes a tubular extension 143, providing journal support for one end of an elongated tubular body I45. The opposite end of the tubular body is telescoped' over, and rigidly secured to a tubular extension I46, of a plug I46,

as by welding. The outer end of the plug I46, has

tion, for accommodating therein, the ends of a torsion rod I55, of square cross section. The body I 55, is shouldered at I55, on which is seated an arm I52, rigidly connected thereto, as by welding. The adjacent end of the tubular body I55, is likewise shouldered, and has rigidly seated thereon, as by welding, a downward y depending operating arm I53. Thus it will be seen that a tendencyto rotate the arms I52 and I55 in opposite directions will result in twisting and building up of torque in the rod I55. By" virtue of this construction, the arm I55, in effect is rigidly attached to the right hand end of the torsion rod I55, and the arm I52, is in eiiect, connected to the left hand end of the torsion rod. In the assembly of the parts, the two arms, I52 and I55, are initially disposed at an angle to each other, and are then moved relatively to each other until they assume a position substantially as seen in Fig. 'I of the drawings, in which condition the rod I55, has been twisted as seen in Fig. 6, so as to preload the torsion rod. The torsion rod in preloaded condition is maintained in such condition by the provision of a stop pin I55, on the arm I59, adapted to be engaged by an abutment I55, is provided with a stud I55, carrying a roller I51, disposed in a-posltion to be engaged by a main operating cam I59 adapted to be power driven by the motor, as will hereinafter appear. Thus, it will be apparent that with the torsion rod I55, in preloaded condition, and due to the abutment shoulder I52, of the arm I52, engaging the stop pin I55, the entire assembly attached to the rock shaft I25, in effect is adapted under certain conditions to move substantially as a single unit in the Process of moving the shoe I5, toward and away from the roll I2. the parts seen in Fig. '1 of the drawings, the power driven cam I59, is disposed in relation to the roller I51, corresponding to a position at which the shoe I5, is caused to assume a position out of engagement with the roll, as seen in dotted lines in Fig. 28. To insure that the shoe moves to such position when the cam assumes the position seen in Fig. 7, we provide a coil spring I55, surrounding the tubular body I55, and having one end surrounding the rea edge of the arm I53, and the opposite end of the spring being anchored in a depending flange I, of a re-enforcing channel I5, secured to the under side of the top of the sheet metal housing of the main supporting housing I5.

, Shoe operating mechanism and interlocking control with roll driving mechanism The shoe operating cam I59, is fixedly secured on a power driven-shaft I52, associated with driving mechanism mounted within a cast housing I59, which mechanism in turn is operably connected with and driven by the rear end extension 3.5", of the shaft of the motor 55. Said mechanism includes a main driven shaft I55, disposed in substantially axial alignment with the rear extension 55', of the motor shaft, and the said ends of said shafts are slotted as indicated at In the position of I55, and 55 respectively, to provide anchorage for the opposite ends of a coil spring I55, which constitutes a flexible coupling for transmitting power from the rnotor 55, to thejdriving mechanism within the housing- I55. The use ofa coil spring as a coupling has two main advantages, in

that it permits accommodation to slight misalignment of the shafts being coupled, and further,

in that it permits the motor to gradually assume the full load. The drive connections from the rearward end of the motor are, as will herein-' after appear, utilized to supply power for moving is in engagement with the roller I51, the maximum load is then being imposed upon the motor 55. In order to utilize a motor of minimum size and power requirements, we employ a flywheel I15, on the rear extension 35*, of the motor shaft. Said wheel tends to cause the armature of the motor to continuously rotate, so that as the cam I59 is rotating in process of moving the shoe into engagement with the roll, the fly wheel effect will provide the additional force necessary, when using a small size motor to cause the peak or high point of the cam to cam against roller I51, to

I cause the shoe to exert pressure against the roll.

In this connection, it will also be noted that the contour of the cam I59, is such that the cam surface, with respect to the axis of the shaft I52, increases gradually, a I comparatively small amount, throughout a range of approximately 180 degrees, so that the load imposed upon the motor in the movement of the shoe is gradual, and permits utilizing a motor of relatively small power size.

The cast housing I53, which contains the drive mechanism for operating the shoe, includes, the rock shaft bearing III, as an integral part thereof, and the housing proper is rigidly secured in position within the main housing I5, to a dependmg plate I1 I, by means of screws I12. The upper end of the plate I1I, has th rock shaft bearing I55, formed as an integral part thereof, as seen in Fig. 1 of the drawings.

The housing I55, is. composed of two main cast members, I15 and I15, adapted to be connected together by machine screw I11. The driven shaft I55, of the driving mechanism is in the form of a headed element, and includes a portion of reduced diameter as indicated at I", as

clearly seen in Fig. 23, journaled in a bearing I15, press-fitted into a boss formed on the hous-' ing part I15, with the head or enlarged portion of said driven shaft disposed in abutting relation to the end of the bearing I15, and is urged in such direction, when driven by the coupler spring I55. The inner end of the reduced portion of the shaft I55, is formed as a pinion I19, which with a projection I55, adapted to seat in a recess.

I55, formed in the housing member I15, as clearly seen .in Fig. 24 of the drawings. Thus, the hub, together with its gear I55, is confined against axial movement'onthe shaft- I52. The opposite cumferentially spaced-apart teeth I90, of a clutch plate I9I, rigidly attached by means of rivets I92, to the adjacent face of the gear I80. The pinion I89, is constantly in mesh with a ear I93, journaled in retained relation on a stub shaft I94,

press-fitted in a boss in the housing member I18,

below the bearing I18". Rigidly connected to the gear I93, is a pinion I95, which in turn-meshes with a gear I98, which is rigidly secured on the cam shaft I82. v

The shaft I82, is journaled in a, bearing I18, of the housing member I18. Supported on the inner end of the cam shaft, as clearly seen in v Fig. 22 of the drawings, is a control disc 200, which serves, as will hereinafter be described, to control'the extent of intermittent rotation of the cam I59, which in turn controls movement of the shoe toward and away from the roll. The disc 200, is press-fitted on, and rigidly connected to a hub "I, which in turn is splined on the extreme end of the shaft I82, so as to permit a limited amount of axial movement of the disc with said hub I, on said shaft I62. The disc is formed with a pair of cam fingers 202, of generally arcuate formation, as seen in Fig. of the drawings, and spaced apart with respect to each other, an amount corresponding to the spacing of the high and low points on the contour of the cam I59.- The card fingers 202, are adapted to be engaged alternately by a spring trip finger 204, secured in keyed relation to the end of a rock shaft 205, journaled in'the housing member I18, as seen in Fig. 24 of the drawings. The opposite end of the shaft 205, projects exteriorly of the housing member I18, and has connected thereto, an arm 208, the outer end of which is connected by a rod 201, to a part of the interlocking control mechanism to be presently described. Mounting in supporting relation to the spring trip finger 204, is a plate 208, likewise keyed to the shaft 205. Normally the operating shoulder 204, of the trip finger is 'disposed in spaced-apart relation to a slight rise or hump portion 208, of the plate 208, as seen in Fig. 19 of the drawings.

The marginal edge of the cam disc 200, extends into an annular groove I88, formed in the outer end of the clutch member I88, beyond the pinion I89. The cam disc, and through its connection, the clutch member. I88, are urged to the 1 position seen in Fig. 24 of the drawings by means of a. coil spring 2I0, surrounding the hub 20I, of the cam disc, and re-acting at one end against the inner end face of a recess or well H5, in the housing member I15,-and its opposite end seat-' ing on a collar 2| I, disposed against the adjacent face of the cam disc 200. Thus, the coilspring 2I0, in addition to exerting an axial pressure against the cam disc, also tends tourge the clutch .member I88, and its pinion I89, into driving relation with the clutch plate I9 I The trip finger 204, is normally disposed in the position seen in Fig. 20 of the drawings, by means of a torsion spring 2I2, seated in a well H5, in the housing member I15, with one end-of said spring anchored to said housing member, and the other end engaging the plate member 208, as clearly seen in Fig. 24. Said spring serves to return the'trip member and plate to the position seen in Fig. 20, after having been moved to the position seen in Fig. 25 of the drawings, by operation of the rod 201.

It will now be apparent that when the rod 201, is operated by movement to the right, as viewed in Fig. 20, it shifts the trip finger 204, to the position seen in Fig. 25 of the drawings, and at which position the finger is moved out of the path of engagement with respect to the cam fingers 202, of the cam disc, and said disc is permitted to move axially on shaft I82, to the position seen in Fig. 24 of the drawings, under influence of the coil spring 2I0, and simultaneously therewith, the clutch member I88, is shifted. into driving engagement with the clutch plate ISI. The instant that .the force is removed from the rod '201, the trip finger 204, and its supporting plate 208, immediately return to the position seen-in Fig. 20 of the drawings, under influence or the compression spring 2I2, with the outer end of the trip finger disposed in position to engage one of the cam fingers 202, causing the adjacent cam finger, during the rotation of the cam disc 200,

to ride camwise upon the outer end of the trip 'finger, and thereby move the cam disc axially outward, as clearly seen in Fig. 22 of the drawings. Incident to such movement of the cam disc, the clutch member I88, is simultaneously disengaged from the clutch plate I9I, thereby arresting rotation of the cam disc 200, the cam shaft I82, and the shoe operating cam I59, which control the movement of the shoe I8.

It is to be understood that the location of the cam fingers 202, to the cam I59, are such that each time that the rod 201, is operated to move the trip finger 204, out of engagement with one of the cam fingers 202, the driving mechanism is set into operation for rotating the shaft I82, and the cam I59, a portion of a revolution, which corresponds to the movement from, what for convenience may be designated as, a low position E of the cam I 59, to thehigh position, indicated at D of said cam I59 and vice versa. In other words, it may be stated simply that when the trip finger 204, is'disengaged, the cam I59, moves from the position seen in Fig. '7 of the drawings to the position seen in Fig. 8 of the drawings, and the next time that the trip finger 204 is disengaged, the cam I59, is moved from the position seen in Fig. 8 of the drawings to the position seen in Fig. 7 of the drawings. As above stated, the position of the cam in Fig. 7 of the drawings corresponds to .a condition wherein the shoe is backed away or out of engagement with the roll I 2, while Fig, 8 of the drawings represents a condition of the parts with the shoe disposed in ooperative pressure engagement with the roll.

Rigidly mounted on the outer end of the cam shaft I82, is a timing disc 2I5, of generally circular contour, provided with a single relatively deepmarginal notch 2I8, which is disposed in close proximity to axial alignment with the low point E of cam I59. Cooperatin with the timing disc 2I5, is an interlocking control lever 2I8, pivotally mounted on a stud 2I9, carried by a bracket 220, fixedly secured to the adjacent end wall of the housing member I18, by means of screws 22I. The control lever has one end positioned immediately below and in contact with the periphery of the timing disc 2I5, and is provided with a notch 2I8, to one side of which is formed an angular detent 222, adaptedtin certain angular positions of adjustment of the member 2I8 to register with and seat in the notch 2", or the timing disc, as seen in Fig. 15 of the drawings. The interlocking lever member 2I8, is preferably formed of spring metal, and is normally disposed as seen inFig. 13 of the drawings, exerting a slight upwardpressure on the periphery of the timing disc 2I5. The opposite edge of the member 2I0, adjacent detent 222, is formed with an upstanding stop lug 225, adapted, when the member 2I0 is in the position as seen in Fig. 10 of the drawings, to engage the adjacent face of they timing disc 2I5,

to limit-the angular or pivotal movement of the interlocking lever member 2I0, in counterclockwise directioh, as viewed in Figs. 10, 11, 12, and 13 of the drawings. A supporting lever 230, is pivotally mounted on the stud 219, and has its outer end connected to a control rod 23I, the opposite end or which rod 'is connected to the depending member I00, associated with the knee operating control member II2, as seen in Fig. 16 of the drawings. The rearward portion of the member 2I8, is provided with a depending lug 218, which is connected by a coil spring 233, to an upstanding lug 230, of the supporting plate 230, tending to maintain the control lever 2I8, and the supporting plate 230, in approximately straight line relation to each other, such as seen in Fig. 11 of the drawings.

The purpose in making control lever 2I8, of spring metal, is to insure. against possible breakage, which might occur if the lever were rigid, and the cam I59 and timing disc 2I5, rotate when the detent 222, of said lever 2I8, is in registration with the notch 2I6, of said timing disc.

Mounted beneath the supporting plate 230, is a trip member 235, also connected to the operating rod 23I, at one end, the opposite end being provided with an upstanding stud 236, on which is mounted a roller 231, adapted to 'be disposed in and follow the contour of a cam slot indi-' cated at 238, formed in' the supporting plate 220, as seen in Figs. 11 and 13 of the drawings. The opposite end of the stud is provided with an enlarged washer 240, overlapping the cam slot and engaging the upper surface of the plate 220, to support the roller in proper relation in the cam slot 238-, as well as supporting said end of the trip member 235. The trip member 235, is provided with a depending lug 235, to which is anchored one end of a coil spring 242, the opp site end of which spring is anchored to a depending lug 230, of the supporting plate '230. This spring connection serves to maintain the roller 231 in yielding engagement with the cam surface of the slot 238, and causes the roller to follow the contour of such surface during the movement of the trip member 235, as may be seen in Figs. 10, 11, 12, and 13 of the drawings. Also mounted on the pivot-pin 2l0, is a trip lever 245, which includes a leg portion 245, slidably mounted on the rod 201, and normally disposed in abutting relation to a nut 201, on the outer end of said rod. Said trip member also includes an upstanding lug 245 projecting through an aperture 220" in the supporting plate 220, and adapted to abut against an edge 01 the opening as seen in Fig. 10 of the drawings, for limiting the position of the trip lever 245, in one direction of movement. The trip lever also includes an arm 245, provided with a depending lug 245, adapted in the position seen in Fig. 11 to engage the depending lug 235, of the member 235.

The control lever 2I8, supporting lever 230,

and the triplever m, are held in assembled relation, against the bracket 220. on the pivot pin 2H1, by a coil spring 2N1. The spring surrounds a sleeve 210', on the pin, and abuts at one end against the underside oi. the control lever 2|8, and at the other end against a washer 2MP, abutting the end of the sleeve, and the parts are held in such assembled relation by a spring clip 2| 9, as seen in Figs. 14 and 16 .of the drawings.

As above described, when the rod 201, i pulled, for example, from the position seen in Fig. 10 of the drawings, to the position seen in Fig. 12 of the drawings, the trip finger 204, is disengaged, and the motor power is then coupled with the clutch I08, for driving the cam shaft I02, and

the cam I59, as above described, and which, as

clearly above stated, completes a partial revolution each time the trip finger 204, is disengaged. The design of the parts is such, that during two successive actions of the trip finger, the cam I50, completes a single revolution.

Operation The interlocking control mechanism between the drives for theroll and the shoe respectively, assumes several difierent positions of adjustment during the cycle of operation of the machine. When the knee control member H2, is in the dotted line position indicated at A, the drive of the drawings, and finally assumes the position I seen in Fig. 13 of the drawings, during which movement, the rod 201 is operated to disengage trip finger 204, and partial rotation of cam I50 is effected for moving the shoe against the roll.

' When pressure on the knee control II2 is'then relieved so, as to permit said member II2 to assume again the position A," the interlocking control mechanism acquires a positionas seen in Fig. 11 of the drawings, and during such movement of the knee control member II2, lever 235 is relatched with lever 245, which conditions the tripping mechanism for subsequent. operation of the shoe. If pressure is additionally relieved on the knee control II2, so as to permit it to assume the full line position indicated at "C in Fig. l of the drawings, the interlocking control mechanism then acquires theposition seen in Fig. 10 of the drawings, during which movement the shoe is in engagement with the roll, and movement is transmitted to the members I08 and I06, which effects engagement of the clutch 51 of the roll driving mechanism for causing the roll to rotate.

It is by virtue of the construction and manner of a pressing operation on articles being worked upon, whereas, when the control member I I2 is permitted to move to the position seen in full lines 

